WO1982003350A1

WO1982003350A1 - Reamer holding device for machining valve seats

Info

Publication number: WO1982003350A1
Application number: PCT/JP1982/000107
Authority: WO
Inventors: Giken Kogyo Kk Honda
Original assignee: Hidroyasu Minoru; Yamashita Hideo; Oguro Tamotsu; Yamagishi Shigeru; Shino Shigenari
Priority date: 1981-04-07
Filing date: 1982-04-07
Publication date: 1982-10-14
Also published as: BE892766A; US4555205A; FR2511281B1; BR8207254A; GB2110130B; JPS57168827A; GB2110130A; FR2511281A1; IT8248164A0; IT1148914B; JPS5911402B2

Abstract

A reamer device for machining the valve seat surfaces of the cylinder heads of an internal combustion engine. It is necessary for the reamer device of this type to feed a blade holder and its driving system axially without unreasonable force during machining. This reamer device employs supporting pins instead of the ball bearings used to support the blade holder during machining in the conventional blade holder, thereby eliminating the unreasonable force applied to the blade holder and its driving system. The axial core of the blade holder (a) is not coincident with that of the spindle (s) during machining. Therefore, the blade holder is coupled via a universal joint (j) to the spindle, and the blade holder can alter its machining angle. A plurality of supporting pins (2) are provided to control the movements of the blade holder during machining and are radially positioned using compressed air and hydraulic oil.

Description

' Specification

Pub-Gut Machiner holding device

Technical field

The present invention relates to a rotating body holding device, and more particularly to a rotating body holding device that is required to be rotatable around an axis that is not coaxial with a drive shaft.

Background art

SUMMARY OF THE INVENTION The present applicant has previously disclosed a cylinder head for an internal combustion engine, which includes a rotating body that carries a machining tool and is non-coaxial with a drive shaft and that also rotates around an axis on a different line. We have proposed a work machine for the valve seat surface (as Japanese Patent Application No. 56-319193).

The configuration and function of the machine tool area according to this proposal will be described below with reference to FIG. 6 and FIG.

Reference numeral M indicates the entire machine tool .In the center of the machine tool M, there is provided a center part and a center part for a reamer for finishing a guide hole of the valve stem guide g. A tool holder with a blade and a tool c, such as a valve cutter that applies a valve sheet Vs to the outer circumference. The tool holder a has a free spin on the power spindle S. On the other hand, a ring-shaped sabot plate P is slidably suspended on a guide bar G extending forward from the multi-head 1 ^. A cylindrical bearing holder d having a self-aligning bear link 'b attached to the inside of the front end is slidably disposed on the front surface of the robot plate P. · It is embraced by a mouth plate つ provided with a collar cylinder e of the holder d and a spin β β υ ' : Kuji Phi, C :. '? I While rotating the drill S, advance the multi-axis head H, insert the reamer into the guide hole of the valve stem guide g, and attach the reamer ^ as shown in FIG. Advance while adjusting to the guide hole position. In the process, the tool holder a is fitted to the self-aligning bearing b. After that, the change in the inclination of the tool holder a is aligned. Bearing: The aligning action of b and the sliding of the bearing holder d are absorbed, and the reamer is sufficiently guided. When arrogant in the hole, the lock cylinder e is actuated, and the bearing holder d is moved to the support bracket P by the best pin. To a constant state, and the size of the blade c is adjusted by the ball stem guide g and the centering bearing b. The valve seat surface was machined with the cutter c while maintaining good concentricity with the guide hole.

However, in the rotating body holding device as described above, the outer diameter of the bearing holder d including the aligning bearing b becomes relatively large and the weight becomes heavy accordingly. However, as described above, the blade holder a is fitted to the alignment bearing b during the progress of the reaming, and the blade holder a is fixed until it is fixed in a fixed state. Centering bearing on a: The weight of b and the bearing holder d became stronger, leaving room for improvement in this respect. Also, the inner surface of the aligning bearing b moves in the ¾ direction when the tool holder a is fitted, so a high-precision clearance is required. In this regard, there was room for improvement.

_ C: 'PI 'Disclosure of the invention'

In view of the above-described problems in the conventional rotating body holding device, the present inventors have determined that the present invention should be effectively determined.The purpose of the present invention is to apply an unreasonable external force to the rotating body. An object of the present invention is to provide a device for holding a rotating body that can stably hold the rotating body without adding thereto and that does not substantially affect the rotating shaft of the rotating body.

A further object of the present invention is to provide a low-cost, versatile rotating device that eliminates the need for nervousness in the clearance between the transfer members during manufacture and use. Provide a body holding device.

In order to achieve the above object, the present invention provides a cylindrical member into which a rotating body can be inserted, and a radially arranged movable member disposed on the inner periphery of the cylindrical member. The present invention also provides a rotating body holding device including a sabot member and D hook means capable of independently holding the sabot member at an arbitrary position.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is an overall view including a semi-longitudinal sectional view of a main part of a rotating body holding device according to a first embodiment of the present invention.

FIG. 2 is a partially cut-away simplified front view showing the essentials of the holding device of FIG. 1,

Fig. 3 is a partially cut side view showing the state immediately before the operation of the machine with the holding device of Fig. 1 crawled! :,

Fig. 41 1 shows the state of the machine tool in Fig. 3 during operation.

£ 'and two four, ο.-ρτ

0 ΙθΦ ' FIG. 5 is a semi-longitudinal sectional view showing a main part of a rotating body holding device according to a second embodiment of the present invention.

FIG. 6 is a partially cut-away side view showing a state immediately before the operation of the same machine tool as in FIG. 3 to which the conventional rotating body holding device is applied,

FIG. 7 is a partially cut-away side view showing the state of the machine tool shown in FIG. 6 during operation.

BEST MODE FOR CARRYING OUT THE INVENTION

FIGS. 1 and 2 showing a rotating body holding device according to a first embodiment of the present invention, and a state immediately before operation of a machine tool when the holding device is applied to the same machine tool as in FIGS. 6 and 7. 3 and 4 showing the state of operation and the state of operation, reference numeral 1 denotes a support cylinder, and in the case of the present embodiment, the support cylinder 1 is a support cylinder of the machine tool. It is formed in a rectangular shape so that it can be directly mounted on the front side of the circular cavity at the center of the plate P, and has a cylinder length substantially equal to the reaming length of the reamer. The outer cylinder 1a is fixed integrally with the plate P, and has an inner peripheral surface that is larger than the outer diameter of the rear part of the blade holder a and that is fixed in the oil cylinder. It consists of an inner cylinder 1b. At the front of the inner cylinder 1b, at least three sabot pins 2 made of soft metal such as gunmetal are provided at predetermined intervals in the circumferential direction so as to be able to freely enter and exit in the shooting direction. The cylinder 1b is fitted so that it can move freely in the radial direction, and the inside of the cylinder wall of the inner section 1b has the radius!比 Ratio for supplying pressure oil to urge servo pin 2 inside and outside

CVPI A relatively large-diameter valve chamber 3a and a narrow path 3b are drilled at the position corresponding to each sabo: "Topin 2 up to the rear end of the inner cylinder 1b. In the chamber 3a, a valve body 4, which is slightly shorter than the valve chamber 3a and whose rear end is flush with the rear end of the valve chamber 3a, is fitted and fixed, and the valve body 4 is located at the center. In addition to having a crossroad 4d, a spherical check valve at the front is urged rearward by a spring 4c to close the front end of the crossroad 4d in the front-rear direction at the rear end position. The clearance 4a can be freely moved back and forth with a clearance between it and the front inner wall of the valve body 4, and the rear part can be checked through the crossroads 4d. A piston 4b provided with an extension for pressing the valve 4a forward is accommodated in the rear inner wall of the valve body 14 in an fp manner so that it can slide back and forth. , Bal The space defined by the front inner wall of the body 4 communicates with the front of the valve chamber 3a, and when the check valve 4a is not at the rear end position, the crossroad 4d and the inner cylinder 1b are connected. A first annular groove 7a provided on the outer circumference of the inner cylinder 1b through the drilled radial through hole 5 and a first annular groove 7a formed in the cylinder wall of the outer cylinder 1a. On the other hand, the space defined by the rear inner wall of the valve body 4 and the back of the piston 4b is open to the rear end of the inner cylinder 1b and the outer cylinder 1a. A second inner wall 1b is provided on the outer periphery of the inner cylinder 1b through an annular space formed by the front surface of the rear inner wall step and the annular packing 8 interposed between the oil tights. It communicates with the annular groove 7 of the inner cylinder 2 and communicates with the second opening 6b opened in the cylinder wall of the outer cylinder 1a. Ning 8

^C;; PI Through a through hole formed in the outer cylinder 1a and a third opening 6c formed in the rear portion of the outer cylinder 1a through the third annular groove 7c formed in the inner wall step 內 at the rear portion of the outer member 1a. I understand.

In the above, the first and third openings 6a and Sc are connected to the lower portions of the oil tanks 9a and 9c via oil lines, respectively. the, that it is supplied pneumatically through the _ι air pressure source a by Ri air full Note1 over f and the first stage pressure reducing valve _Γ via the second-stage pressure reducing valve r ₂ and the switching valve 1 O a. On the other hand, the second opening 6b is connected to the lower part of the oil chamber of another oil tank 9b via an oil line, and the upper part of the oil pressure Thus, the air pressure passing through the air filter 及び and the first-stage decompression valve is supplied only through the switching valve 1Ob. Switching valve when holding device is not operating

10a and 1Gb are in the state shown in Fig. 1, and the air line on the side reaching oil tank 9a is released to the atmosphere and reaches the oil tank 9c. The air line on the side is connected to air pressure A via _two pressure reducing valves r ₂ , Γ !. For this reason, relatively low-pressure oil enters the third opening 6c from the oil tank 9c and is distributed to each narrow path 3b through the third annular groove 7c. Acts on the underside of Tobin 2. On the other hand, the air line leading to the oil tank 9b is connected to the air pressure source A via a single valve, so that the oil tank 9b is connected to the second opening. A relatively high-pressure oil enters and is distributed to the rear of each valve body 14 through the second annular groove 7b and acts on the back of the piston 4b in each valve body 14. , This

CV: PI As a result, the check valve 4a is pushed to the solid line position against the spring force of the spring 4c, so that the oil in the valve chamber 3a is oiled through the crossroad 4d. The support pin 2 can be returned to the tank 9a freely, and each support pin 2 is pushed upward, that is, radially outward of the inner cylinder 1b by the hydraulic pressure in the narrow path 3b, and 1 It will be kept in the retracted position in the execution position in the figure.

In FIG. 1, reference numeral 11 denotes an air vent plug for a buried portion of the support pin 2, 12 denotes a stop pin of the support pin 2, and 13 denotes a valve body 4. It is a stop pin for

FIG. 3 shows that a plurality of the above-mentioned servo cylinders 1 are attached to the center of the front surface of a servo plate p of the machine tool, and the multi-axis head H is advanced to mount the servo plate P on the machine tool. This shows the state immediately before machining when the lead li is set on the guide boss on the jig D where the set li is set, and the spindle S is rotated during machining. The tip of each reamer trapped by this moves into the pick-up hole of the valve guide g, and cuts the inner surface of the guide hole. At this time, the installation of the vanole guide g is not appropriate, or there is some variation in the position of the guide hole, or depending on the workpiece. The tool holder a holding the reamer is deflected to the spindle via the self-joint j, even if the variance varies. As shown in Fig. 4, it is free to move in any direction (up, down, left, or right) as shown in Fig. 4 in response to slight deviation or inclination of the guide hole position. — マ ϋ 'fits well in guide holes without being subjected to excessive force

C.VIPI 0 Finish the surface

Meanwhile, the blade holder a will move forward in the sabot cylinder 1. When the tip of the reamer ^ begins to protrude from the guide hole of the valve guide g and the rear part of the tool holder a reaches the front end of the support cylinder 1, the machine tool core is The switching valves 10a and 1Ob are electrically switched by a timer or a limit switch incorporated into the oil tank 9a. The air line on the side is connected to the air pressure source A, and the air line on the side reaching the oil tanks 9b and 9c is opened to the atmosphere. Then, a relatively low-pressure oil from the oil tank 9a is applied to the crossroads 4d 'of each valve body 4 via one opening Sa, the first annular groove 7a and the through hole 5. The piston-b is retracted to the position indicated by the dotted line in FIG. Thus, the sabot bin 2 moves inward, that is, in the direction of the blade holder a, as shown by the dotted line in FIG. Abut At this time, the pressure oil acting on the lower portion of each servo pin 2 is transmitted through the narrow path 3b, the third annular groove 7c and the third opening 6c, and the fuel tank is removed. Returned to 9c

In this way, as shown to the second physician, the knife holder a keeps its outer peripheral portion in the sabot cylinder 1 at an arbitrary position, and the outer peripheral portion thereof is spaced apart by a predetermined number at equal intervals. The boat pin 2 allows you to be held tightly from the outside. That is, the rotation axis of the blade holder a, which is a rotating body, is not aligned with the center of the inner cylinder 1b. Even if the clearance between the outer peripheral surface of the blade holder a and the inner wall of the inner cylinder 1b is offset in either direction, each servo pin 2 is still Then, it protrudes by an amount corresponding to the clearance at the corresponding position of, contacts the blade holder a, and holds it.

In addition, even if the outer peripheral surface of the tool holder a is slightly away from the servo bin 2 at a certain arbitrary position, the servo bin 2 is still in the oil pressure of the valve chamber 3a '. Therefore, even if the outer peripheral surface of the tool holder a acts to push in a certain servo pin 2, the support pin 2 that once protrudes is not compressed. Do not pull in while being supported by the sex oil, but only generate a fluid pressure in the valve chamber 3a that is appropriate for the pushing force. .

Since this phenomenon occurs for each of the servo bins 2 arranged on the inner peripheral wall of the inner cylinder 1b, the cutter holder a and the rimmer should maintain a constant axis. Will be supported by Sabotot Pin 2.

In the above statement, the check valves in each valve

4a 、 When the corresponding servo pin 2 is completely ejected, the valve 4a including the pressure difference and the like based on the orifice effect around the valve 4a is removed. If the resultant force of pushing the valve 4a 'back by the spring force of the spring 4c and the hydraulic pressure in the valve chamber 3a overcomes the resultant force of the force pushing forward, Moving along the dotted line in FIG. 1 and closing the crossroads 4d, the support pin 2 is then moved until the valve 4a is opened again.

Γ. · Ρι

Λ The state will be locked.

In such a state, if the spindle S is further advanced slightly together with the multi-axis head H, the cutter holder a becomes the support pin.

2 While rotating inside, it moves by that amount, and the tool c on the tool holder a Forces the valve sheet Vs to process the sheet surface 0

At that time, the cutter C has a reamer bearing on the valve guide g on the front side, and the cutter holder a is bearing on the rear side by the servo bin 2 on the rear side. Without this, it is possible to machine a highly round valve seat surface while maintaining concentricity with the valve stem guide hole.

In this way, after the machining of the valve seat Vs is completed, the multi-axis head H is slightly retracted, the switching valves 10a and 0b are switched again, and the oil tank 9 is turned off. The air line leading to a is released to the atmosphere, and the air line leading to oil tanks Sb and 9c is connected to the air pressure source A.

Then, a relatively high-pressure compressed air is supplied to the oil tank 9, and a high-pressure oil corresponding to the compressed air enters the support cylinder 1 from the second opening Sb and the second annular groove 7. The valve 4b is distributed to the rear of each valve 4 through b, so that the piston 4b is pushed out to the position indicated by the solid line in FIG. 1 and the check valve 4a is pushed forward. When opened, the crossroads 4d communicate with the valve chamber 3a. At the same time, a relatively low-pressure oil from the oil tank 9c enters the support cylinder 1 through the third opening 6c, and enters the inner cylinder 1 via the third annular groove 7c. distributed to each narrow path 3 b in b; c; -n As a result, each of the support pins 2 is moved downward to return to the position indicated by the solid line in FIG. The holding state of da a is released.

At this time, the oil in the valve chamber 3a is returned to the oil tank 9a from the first opening 6a through the center and the crossroads 4d in the valve body 4. As a result, the initial non-operating state is obtained.

Next, a description will be given with reference to FIG. 5 showing a rotating body holding device according to a second embodiment of the present invention. For convenience of explanation, the same or similar parts as those in the first embodiment will be denoted by the same reference numerals to avoid duplication of explanation. The sabot cylinder 1 is composed of a rectangular outer cylinder 1a and an inner cylinder fixedly inserted into the outer cylinder 1a. In the present embodiment, the large-diameter valve chamber 3a of the inner cylinder 1b includes: In place of the valve body 14 in the previous embodiment, a stem valve having a flow channel 104a at the front end communicating with the valve chamber 3a is provided.

Each of the sub-bins 2 has a relatively high oil pressure applied to the rear end of the stem valve 104 when each sub-pin 2 projects. Is locked. A pad member 102 is provided on the inner end of the support pin 2.

It should be noted that the above embodiment differs from the machine tool inspection in which the guide hole of the valve stem and the sheet surface of the valve seat in the cylinder head are machined. As described above, the rotating body holding device according to the present invention is required to be rotatable with respect to the driving shaft even around a non-common axis. Rotating body —In general, the same applies.

As is clear from the above description, according to the present invention, the rotating body is stably supported without causing run-out, and the precision of rotation is improved as in the case of the conventional alignment bearing. There is no need to consider the balance, and even if the sabot pin is worn due to contact with the rotating body, it is possible to protrude by the amount of wear, even if the sabot pin is worn by contact with the rotating body. The support function of the rotor does not decrease, and the sabot pin is retracted while it is not necessary to support the rotating body, so that unnecessary load is not applied to the rotating body and the axis is No change or bleeding o

Industrial applicability

The present invention does not substantially affect the rotation axis of the rotating body, and the tilling body which does not need to be nervous in the clearance between the moving members during manufacture and use. Provide a holding device. Therefore, according to the present invention, it is possible to obtain a rotating body holding device that maintains the d [rotation] with high precision, while being highly useful and low in cost.

Claims

The scope of the claims ·

1. A cylindrical member with a rotating body that can be freely inserted, and

At least three sabot members, which are disposed on the inner periphery of the cylindrical member and are movable in a substantially radial direction,

And mouth means capable of independently holding the sabot member at an arbitrary position.

Retaining device for rotating body.

2. The .pi.-means is provided with the same number of hydraulic ports as the number of sabot members provided for each of the support members, and one for each of the hydraulic port mechanisms. 2. The holding device according to claim 1, wherein the holding device comprises a hydraulic supply mechanism.

3. The second aspect of the present invention, wherein the hydraulic port mechanism is provided in a cylindrical wall of the cylindrical member, and the hydraulic supply mechanism is provided outside the cylindrical member. Retention described in section

4. Each one of the sabot members has an embedding portion movably fitted in a radial direction of the cylinder member in a cylinder wall of the cylinder member, and the embedding portion receives hydraulic pressure. 4. The holding device according to claim 3, wherein the holding device has first and second pressure receiving surfaces for pressing the sabot member inward and outward in the radial direction, respectively.

5. Each of the hydraulic opening mechanisms is connected to a first and a second oil chamber respectively partially defined by the corresponding first and second pressure receiving surfaces. And a second hydraulic circuit The hydraulic supply mechanism is capable of selectively switching the first predetermined hydraulic pressure and the second predetermined hydraulic pressure of just high pressure to each other to supply the first and second extraction circuits. The holding device according to claim 4, wherein the holding device is characterized in that:

6. The hydraulic locking mechanism includes a check valve member constantly urged to the inlet and the closing side of the first oil chamber, and a drive mechanism for driving the check valve member to the open side. 6. The holding device according to claim 5, wherein the holding device includes a screw member.

7. The piston member receives the hydraulic pressure and

And third and fourth pressure receiving surfaces for pressing the check valve member toward the open side and the closed side, respectively, of the check valve member, and the hydraulic locking mechanism is provided on the third and fourth pressure receiving surfaces. The third and fourth hydraulic circuits that respectively communicate with the third and fourth oil chambers, which are respectively partially defined, are decoupled, and the fourth hydraulic circuit is connected to the first hydraulic circuit. The hydraulic pressure supply circuit is capable of supplying a third m constant hydraulic pressure higher than the first predetermined hydraulic pressure and the second predetermined hydraulic pressure to the third Huai pressure circuit. The holding device according to claim 6, wherein

8. The hydraulic supply structure includes a first connection state for supplying the first, second, and third predetermined hydraulic pressures to first, second, and third hydraulic circuits, respectively, and a first and second predetermined hydraulic pressures. = 2 and 3 and a second connection state for supplying to the first hydraulic circuit, respectively.When the rotating body is held, the rotating body is in the second connection state, and when the holding is released, the second connection state is used. Switch off the bubble pressure supply system to the connection state of 1.

■ Β υ Κ 4 Hi _ C;-PI 8. The holding device according to claim 7, wherein the holding device is provided with switching means for changing.

W top 4

0 ;: P1

, W ⁰ Summary Form

A cylindrical member (<< 1) into which a rotating body can be freely inserted, at least three sub-bottom parts 2) arranged around the inner periphery of the cylindrical member and movable in a substantially radial direction; A rotating body holding device consisting of a locking means (3a, 3b, 4a, 4b, 10a10b) capable of independently holding a sabot member at an arbitrary position.

A rotating body that is required to be rotatable around an axis that is not coaxial with the drive shaft can be held without substantially affecting the rotating shaft. · When used, there is no need to be nervous about the clearance between moving parts, so it is versatile and low cost.

C-PI

V? :? 0